JP3309726B2 - Outer mirror device for vehicles - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a vehicle outer mirror device for rotating a shaft carrying an outer mirror between a use position and a storage position.

[0002]

2. Description of the Related Art Conventionally, there is known an outer mirror device for a vehicle in which a shaft carrying an outer mirror is rotated between a use position and a storage position. This vehicle outer mirror device has a drive mechanism for rotating and driving a shaft, and a case that incorporates the drive mechanism and is fixed to a vehicle body. The drive mechanism includes a rotation transmission mechanism that transmits rotation of the drive motor to the shaft. The rotation transmission mechanism has an insertion hole that is inserted into the shaft so as to be relatively rotatable, and is driven by a drive motor. The rotation transmission mechanism is inserted into the shaft so as to be integrally rotatable and detached from the cylindrical drive gear. As possible, the cylindrical drive gear is engaged and engaged by the biasing force of a spring from its axial direction to transmit the rotation of the cylindrical drive gear to the shaft during mesh engagement, and to rotate the cylindrical drive gear during non-mesh engagement. And a disk-shaped clutch holder that cuts off the transmission of rotation of the cylindrical drive gear by rotating relative to each other while being fitted into (see, for example, Japanese Patent Application No. 6-170912).

[0003]

However, in this conventional outer mirror device for a vehicle, when the disk-shaped clutch holder is relatively rotated, the meshing engagement portion of the disk-shaped clutch holder is entirely formed on the facing surface of the cylindrical drive gear. The sliding resistance is large when the disc-shaped clutch holder and the cylindrical clutch holder rotate relative to each other, so that the disc-shaped clutch holder and the cylindrical drive gear are re-engaged and engaged. When the drive motor is driven to rotate the cylindrical drive gear relative to the disc-shaped clutch holder, there is a problem that the drive current of the drive motor increases. Further, when the disc-shaped clutch holder is relatively rotated, the meshing engagement portion comes into contact with the inner peripheral side of the facing surface portion of the cylindrical drive gear or the outer peripheral side of the facing surface portion so that the contact portion is constant. In addition, there is also a problem that a stable rotation cannot be obtained at the time of relative rotation between the disk-shaped clutch holder and the cylindrical driving gear since a stable sliding resistance cannot be obtained due to a large variation in the sliding resistance.

The present invention has been made in view of the above circumstances, and has as its object to reduce sliding resistance during relative rotation between a cylindrical drive gear and a disk-shaped clutch holder, and to vary the sliding resistance. The present invention provides an outer mirror device for a vehicle, which can reduce the output of a drive motor, and further reduce the size and cost.

[0005]

A first aspect of the present invention.
In order to solve the above problem, the vehicle outer mirror device described in (1) is supported by a case in which a shaft that carries the outer mirror and is rotated between a use position and a storage position is fixed to a vehicle body, and the case A rotation transmission mechanism for transmitting rotation of a drive motor to the shaft is provided therein, the rotation transmission mechanism being rotatable relative to the shaft and being driven by the drive motor; and a cylindrical drive gear; A meshing engagement portion meshed and engaged by the biasing force of a spring from the axial direction thereof, and transmits the rotation of the cylindrical drive gear to the shaft at the time of meshing engagement, and the cylindrical shape at the time of non-meshing engagement. A disc-shaped clutch holder that cuts off the rotation transmission of the cylindrical drive gear by rotating relative to the drive gear, wherein the cylindrical drive gear is Has opposed face portion opposed to the engaging portion each other seen in the the counter surface, the disk-shaped clutch holder
A circle in which the meshing engagement portion contacts and slides during relative rotation
Relative rotation of the arc-shaped sliding part and the disc-shaped clutch holder
Sometimes an arc shape that forms a gap between the meshing engagement part
A concave portion is provided, and the arc-shaped sliding portion is formed on a side close to the shaft.

According to the outer mirror device for a vehicle according to the present invention, when the cylindrical drive gear and the disk-shaped clutch holder rotate relative to each other, only the arc-shaped sliding portion comes into sliding contact with the meshing engagement portion of the disk-shaped clutch holder. Therefore, the cylindrical drive gear and the disk-shaped clutch holder rotate relatively stably. In addition, since the contact area between the cylindrical drive gear and the disk-shaped clutch holder is smaller than before, the sliding resistance can be reduced.

[0007]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a vehicle outer mirror device according to the present invention will be described below with reference to the drawings.

In FIG. 1, 1 is a stay, 2 is a shaft, and 3 is an upper case for a housing. An outer mirror (not shown) is attached to the tip of the stay 1. The base end of the stay 1 is fixed to the mounting flange 5 by welding. The shaft 2 has an engaging flange portion 6 and a columnar portion 7 as shown in FIGS. Four bolt insertion holes 5a are formed in the mounting flange 5, bolt screw holes 8 are formed in the engagement flange portion 6 corresponding to the formation positions of the bolt insertion holes 5a, and the mounting flange 5 is formed in the engagement flange portion. 6 is fastened by bolts 9. In this one,
Since the shaft 2 and the stay 1 have a separate structure, the outside mirror can be replaced according to the type of vehicle. As shown in FIG. 3, the engaging flange portion 6 has a circular recess 10 at its upper surface and its center, and has ball guide grooves 11 and 12 at its lower surface and its peripheral portion as shown in FIG. Have. The ball guide grooves 11 and 12 are formed in an arc shape, and regulate the rotation angle of the shaft 2 between the use position (forward tiltable) of the vehicle door mirror 4 and the storage position (rearward tiltable). The ball guide grooves 11 and 12 have different radial distances from the center of the shaft 2. Thereby, the tilting angle of the shaft 2 can be set to 180 degrees or more. A step 14 for raising the shaft 2 in cooperation with the ball 13 is formed at the end of the rotation area of the ball guide grooves 11 and 12, as shown in an enlarged manner in FIG. This step 1
4 has an inclined surface 14a and a stopper surface 14b. The stopper surface 14b sets the rotation angle of the shaft 2 from the storage position to the use position. Here, the rotation angle is 120
Degrees. The inclination angle of the stopper surface 14b with respect to the horizontal line 14c is set larger than the inclination angle of the inclined surface 14a with respect to the horizontal line 14c. When a predetermined force or more is applied to the shaft 2, the ball 13 moves over the step of the stopper surface 14 b and relatively moves to the bottom surface 6 a of the engagement flange portion 6. The columnar portion 7 of the shaft 2 has a D-shaped cross section and has a flat surface 7a. The lower end of the columnar part 7 is a small diameter column part 7b. A washer 1 is provided on the columnar portion 7 of the shaft 2.
5, the O-ring 16, and the bush 16 'are inserted. As shown in FIG. 2, the bush 16 'of the shaft 2 is relatively slidably fitted with a washer abutting portion 15a with which the washer 15 is abutted, an O-ring abutting portion 15b with which the O-ring 16 is abutted, and a bush 16'. And a bush fitting portion 15c. As shown in FIG. 2, a clearance H is provided between the engagement flange 6 and the upper surface of the upper case 3 to prevent the engagement flange 6 from being fixed to the upper case 3. The upper surface portion T of the upper case 3 is inclined so as to promote the flow of rainwater as shown in FIGS. Further, even if sand, dust, or the like enters between the engagement flange portion 6 and the upper case 3, it easily falls from the upper surface portion T. The washer 15 receives the load of a spring to be described later and the upper case 3 and the washer contact portion 1.
The shaft 2 slides between the washer 5a and the shaft 5a, but the sliding resistance of the washer 15 increases due to burrs generated on the inner peripheral side and the outer peripheral side of the washer 15. In order to reduce the sliding resistance, an annular relief groove G is formed in the shaft 2 and the upper case 3.

As shown in FIGS. 6, 8, and 9, the upper case 3 has a central hole formed with an insertion hole 17 of the shaft 2, a circular recess 17a for receiving the washer abutment portion 15a, and an O-ring abutment portion 15b. Circular recess 17b for receiving and bush 16
'Receiving recess 17c. As shown in FIG. 8, on the upper surface of the upper case 3, an annular peripheral wall 3A for ensuring a clearance G is formed so as to surround the circular recess 17b. Hemispherical ball mounting holes 3a, 3a are formed in the annular peripheral wall 3A at locations facing each other. Connect the ball mounting holes 3a, 3a to the upper case 3.
, Dust can be prevented from accumulating in the ball guide grooves 11 and 12, and the ball 13 is positioned in the ball mounting holes 3a and 3a at the time of assembling.

FIG. 10 shows a side of the upper case 3 to which the vehicle body is attached.
As shown in FIG. 11, a flat portion 3B is formed.
12, a screw hole 3C, a breathing hole 3D, and a harness withdrawal hole 3E are formed as shown in FIG. The harness draw-out hole 3E is formed in an abutment surface 3F which abuts against an abutment surface of a lower case described later. This harness draw-out hole 3E
The harness 3G of the printed circuit board mentioned later is drawn out. An inverted U-shaped canopy 3H, 3I is formed in the flat portion 3B above the breathing hole 3D and the harness drawing hole 3E. The eaves 3H and 3I serve to prevent water from entering the upper case 3 through the breathing hole 3D and the harness drawing hole 3E. Further, since the harness draw-out hole 3E plays a role as a guide hole of the harness 3G, it contributes to improvement of workability at the time of assembly. The screw holes 3C are used to fasten the vehicle body mounting bracket 3J shown in FIG. In this embodiment, screw holes 3
Although six C are formed, the vehicle body mounting bracket 3J
Are appropriately selected and used according to the conditions.

The vehicle body mounting bracket 3J has a support base 3K for supporting a lower case, which will be described later, and a fastening plate 3M attached to the upper case 3 via a screw member 3L as a fastening member. A screw member 3 is attached to the fastening plate 3M.
Two holes 3N for L insertion are formed, and when this type of vehicle body mounting bracket 3J is used, these two holes 3N are formed.
A screw hole 3C corresponding to N is used. A boss 3P for attachment to the vehicle body is formed on the fastening plate 3M, and a bolt and a nut (not shown) are screwed through a bolt hole 3Q formed on the attachment boss 3P, whereby The vehicle body mounting bracket 3J is fixed to the vehicle body. Note that a screw hole 3R is formed in the support base 3K, and the support base 3K is screwed into a screw hole of a lower case described later by screwing a screw member 3S as a fastening member through the screw hole 3R. Fixed. The lower case and the upper case 3 are fastened by one of the screw members 3S.

An upper portion of the upper case 3 has a flat portion 3B.
As shown in FIGS. 1 to 3, 6, 8, 9, and 12, a mounting recess 19 for the stopper member 18 is formed. The stopper member 18 is formed in a T shape when viewed from the front, and includes a mounting plate portion 18a and an engagement plate portion 18b. The engagement plate portion 18b has an arc shape that curves along the outer shape of the engagement flange portion 6 when viewed from above. A screw insertion hole 18c is formed in the mounting plate portion 18a, and a screw insertion hole 1c is formed in the mounting recess 19 on the back surface of the upper case 3.
A screw threaded hole 19a (see FIG. 6) is formed corresponding to 8c. The stopper member 18 is a screw member 18 shown in FIG.
It is fixed to the upper case 3 by d. Upper case 3
A pair of reinforcing projections 3T is formed on both sides of the mounting recess 19 on the upper surface of the mounting recess 19. This reinforcing projection 3T
Has an arc surface 3T 'along the arc shape of the engagement plate portion 18b. Further, on the upper surface of the upper case 3, the reinforcing projections 3 are provided.
Receiving portion 3 receiving engagement plate portion 18b from below adjacent to T
X is formed. The receiving portion 3X and the annular peripheral wall 3A are connected via a step 3V.

As shown in FIG. 1, a disc-shaped clutch holder 22 is inserted through the columnar portion 7. The disc-shaped clutch holder 22 has an oval insertion hole 22a at the center thereof. As shown in FIG. 14, an engagement protrusion 22b is formed around the insertion hole 22a on the peripheral portion 22c of the disc-shaped clutch holder 22. Engaging projection 2
Here, 2b is formed every 120 degrees and has a chevron shape. This disk-shaped clutch holder 22 is
And is inserted through the shaft 2 so as to be integrally rotatable.

The cylindrical drive gear 23 is shown in FIG.
As shown in (b), the teeth 23a, the circular insertion holes 23b, the engagement recesses 23c, and the annular ribs 23 for positioning the springs.
d and an opposing surface portion 23e. The engagement recess 23c is shown in FIG.
As shown in FIGS. 5 (a), 16 (a) and 16 (c), it has a shape corresponding to the engagement protrusion 22b. The shape of the engagement recess 23c and the engagement protrusion 22b sets the engagement force between them.

The shaft 2 is inserted through the insertion hole 23b, and the drive gear 23 is rotatable relative to the shaft 2.
As shown in FIG.
Is urged downward by, the cylindrical drive gear 23 and the disc-like clutch holder 22 is fitted detachably from the axial direction, the engaging projection 22 of the disk-shaped clutch holder 22
b is opposed to the facing surface portion 23e, and FIG.
As shown in (b), they are always engaged.

The disc-shaped clutch holder 22 transmits the rotation of the cylindrical drive gear 23 to the shaft 2 when meshed and engaged with the cylindrical drive gear 23, and is engaged with the cylindrical drive gear 23 when meshed and disengaged. This cylindrical drive gear 23
Rotates relative to the shaft 2 to interrupt transmission of rotation from the cylindrical drive gear 23 to the shaft 2. The cylindrical drive gear 23 has a disk drive gear 23 and a clutch holder 2 on the inner peripheral side of the opposing surface portion 23 e near the shaft 2.
An arc-shaped sliding portion 23f is formed as shown in FIG. An arc-shaped recess 23g is formed in an opposing surface portion 23e between the arc-shaped sliding portion 23f and the tooth portion 23a. This arc-shaped recess 23g is used for the disc-shaped clutch holder 2
A gap is formed between the second engaging protrusion 22b and the second engaging protrusion 22b, and serves as a non-contact portion for reducing the sliding resistance of the engaging protrusion 22b of the disc-shaped clutch holder 22. The arc-shaped sliding part 2
An inclined surface 23h that guides the engagement protrusion 22b toward the engagement recess 23c is formed at both ends of 3f.

The upper end 24a of the spring 24 is in contact with the lower surface of the washer 25, and the lower end 24b is in contact with the upper surface of the cylindrical drive gear 23. As shown in FIG. 1, the washer 25 includes a D-shaped hole 25a, a receiving surface 25b, and an annular peripheral wall 25c. The washer 25 rotates together with the spring 24 and the shaft 2 when the shaft 2 rotates. Thereby, generation of abnormal noise due to rotation of the spring 24 is reduced. The receiving surface 25b of the washer 25 has an annular step, so that the sliding contact resistance with the case 3 is reduced.

As shown in FIGS. 2, 6, 7, 10, and 11, a housing space 26 for a drive mechanism 27 is formed in the upper case 3. The driving mechanism 27 includes a motor 28, a printed circuit board 29, and a plate member 3 as shown in FIG.
0, a worm 31, a helical gear 32, and a worm 33. Worm 31 is helical gear 3
2, the helical gear 32 rotates integrally with the worm 33, the worm 33 meshes with the drive gear 23, and the worm 31, the helical gear 32, the worm 33, and the cylindrical drive gear 23 transmit the rotation of the motor 28 to the shaft 2. It constitutes a rotation transmission mechanism. Also, as shown in FIGS. 10 and 17, the upper case 3 has pin holes 3a ', 3a' for fixing the plate member 30, and the plate member 30.
, 3h, 3i, positioning holes 3m, 3n, and three screw holes 3x shown in FIGS.

FIG. 1 and FIG.
8, as shown in FIG. 19, fitting pins 30a, 30a fitted to the pin holes 3a ', 3a', the motor mounting portion 30b,
The insertion projections 30c, 30c and the guide projection 30d of the printed board 29 are formed. As shown in FIGS. 19 and 20 to 23, the side of the plate member 30 has a harness 3G.
Are formed to prevent the harness 3G from loosening and swaying. The motor mounting portion 30b has mounting screw holes 30f, 30f for the motor 28, an insertion hole 30g for a joint member 40 (see FIGS. 1, 24, and 25) for directly connecting the output shaft of the motor to the worm gear 31,
An insertion hole 30h through which the oval-shaped shaft portion 31a of the worm gear 31 is inserted, and a guide portion 30i of the worm gear 31 are formed. The motor 28 is fixed to the motor mounting portion 30b by screws 28a ', 28a' as shown in FIGS. The joint member 40 has an insertion hole 40a for the shaft portion 31a of the worm 31, as shown in FIGS.
A play is provided between the shaft 31a and the insertion hole 40a as shown in FIG. Thereby, the worm gear 31
The starting torque of the worm gear 31 and the helical gear 32 can be prevented.

On the lower surface of the plate member 30, as shown in FIGS.
(See FIGS. 1 and 11) A pair of fitting portions 3 for fixing
0j and 30k are formed, and a pair of fitting portions 30j and 30k are formed.
The space between them is an installation space 30l for the worm 33. Each of the fitting portions 30j and 30k has an opening for inserting a bush having a U-shaped cross section, and each of the fitting portions 30j and 30k has a worm gear 33.
The shaft portions 33a and 33b (see FIG. 11)
It functions as a pair of bearings supported via 42. The bush 42 is guided to the fitting portion 30j.
The movement restricting ribs 30m and 30n are formed to face the both end surfaces to restrict the movement in the axial direction. As shown in FIG. 26, the pair of movement restricting ribs 30m and 30n have a C-shape having a wide lower part and a narrow upper part.
Is easy to guide. The movement restricting rib 30 for restricting the axial movement of the bush 41 is provided on the fitting portion 30j.
o is formed. A shaft portion 33a of the worm gear 33,
The end face of 33b is in contact with the balls 36,36. The plate member 30 has an arc-shaped positioning outer cylinder 30p and an arc-shaped positioning inner cylinder 3 opposite to the motor mounting portion 30b.
0q is formed. The positioning outer cylinder 30p and the positioning inner cylinder 30q are concentric with the insertion hole 30h. A lower case 4 is provided between the positioning outer cylinder 30p and the positioning inner cylinder 30q.
3 is an arc-shaped guide recess 30r for guiding the arc-shaped positioning cylinder 43a. Positioning tube 43a
Is also concentric with the insertion hole 30h. The plate member 30
The lower surface of the protection surface portion 30s for protecting the helical gear 32
Are formed.

As shown in FIG. 27, the lower case 43 has a bearing cylinder 43b for the shaft 2, a fitting wall 43c for the upper case 3, and pins 43d and 43d fitted to the pin holes 3m and 3n of the upper case 3. , Bush holding portions 43e and 43f (see also FIG. 28) for holding the bushes 41 and 42, and screw holes 43x, 43y and 43z are formed. A bush 44 is fitted to the bearing cylinder 43b as shown in FIG. 2, and the small diameter column portion 7b of the shaft 2 is fitted to the bush 44. An E-ring 45 is mounted on the columnar portion 7 immediately above the small-diameter columnar portion 7b of the shaft 2. The E-ring 45 plays a role of supporting the drive gear 23 and the disc-shaped clutch holder 22 against the urging force of the spring 24. As shown in FIG. 27, a shaft hole 43 supporting the shaft 31b of the worm gear 31 concentrically with the positioning cylinder 43a.
g is formed.

As shown in FIG. 30, the worm gear 31 has a washer 31c integrally with a shaft portion 31b. However, this washer 31c may be separate as shown in FIG. A resin washer 31d is fitted to the shaft portion 31a. 31e is an oval-shaped portion 31f of the worm gear 31
The washer 31 d is integrally rotated with the worm gear 31. Worm gear 31
Is positioned and supported between the plate 30 and the lower case 43 by fitting the positioning cylinder 43a and the guide recess 30r. The bearing wall of the through hole 30h of the motor mounting portion 30b and the bearing wall of the shaft hole 43g of the lower case 43 form a sliding surface on which the washers 31c and 31d of the worm gear 31 slide in contact with FIGS. The washer 31d is made of a bake material, whereby the wear resistance is improved, and the operating noise based on the rotation of the worm gear 31 is reduced. Further, since the washer 31c and the washer 31c are provided to receive a load in the thrust direction, the size, shape, and material of the washer 31c are changed so that the bearing wall portion of the shaft hole 43g of the lower case is formed. Can be changed and adjusted, and the output torque difference between the output torque due to the rotation of the worm gear 31 in the storage direction of the shaft 2 and the output torque due to the rotation of the worm gear 31 in the use direction of the shaft 2 is reduced. can do. In other words, the vehicle outer mirror device having the structure described in Japanese Patent Application No. 6-170912 has a worm gear 31.
Since the end face of the shaft portion 31b is received by the ball, the output torque difference depending on the rotation direction of the worm gear 31 can be solved. Furthermore, worm gear 3
1 is a structure in which a load in the thrust direction is received by a washer, so that both shaft portions 31a and 31b of the worm gear 31 are provided.
It is also possible to reduce the wear of the wall surfaces of the pair of bearing wall portions that support the bearing.

As shown in FIG. 29 and FIG. 34, positioning pins 46
46 are formed. The positioning pins 46 are fitted into positioning holes (not shown) formed in the support base 3K of the vehicle body mounting bracket 3J shown in FIG. Drain holes 47, 47 are formed in the lower case 43 on the vehicle body mounting side as shown in FIG. The drain holes 47 extend from the abutting surface 43p of the lower case 43 where the abutting surface 3F of the upper case 3 abuts to the lower surface 43q of the lower case 43. As shown in FIGS. 35 and 36, the lower case 43 has a cross section inclined toward the vehicle body mounting side, and has a structure in which water such as rainwater that has entered the case is easily discharged from the drain hole. The motor 28 and the printed circuit board 29 are connected to the upper case 3
Is positioned above the abutting surface 3F, and even if rainwater or the like enters, care is taken to prevent electric components such as the motor 28 and the printed circuit board 29 from corroding due to the rainwater and the like.

As shown in FIGS. 1, 3, and 4, the engagement flange 6 has an engagement notch 6z formed on the outer periphery thereof. The engagement plate portion 18b of the stopper member 18 faces the rotation region of the engagement notch 6z. The shaft 2 is a motor 28
Is driven to rotate. The rotation angle of the shaft 2 between the use position and the storage position is usually the ball guide groove 11, 12.
Is determined by the ball rotation range. The motor 28 is turned off, for example, at a use position or a storage position by detecting a lock current (overcurrent) flowing through the motor 28 by an overcurrent detection circuit (see FIG. 37) of the printed circuit board 29. When the ball 13 is located at the step 14, the shaft 2 is slightly raised, so that the spring 24 is slightly compressed,
The pressing force of the flange portion 6 against the ball 13 increases, and the shaft 2 is held without rattling at the use position or the storage position. Note that the driving torque of the motor 28 is set to a magnitude that is less than that required for the ball 13 to get over the stopper surface 14b.

As shown in FIG. 37, the driving circuit includes fixed contacts 51a, 51b, 5
2a, 52b, a switch circuit composed of linked movable contacts 53a, 53b, first diodes 54, 55 for rectification connected to the motor 28, and a first PTC as overcurrent detection means.
The motor 28 is roughly constituted by an element 56 and a second PTC element 57, and the rotation of the motor 28 is stopped by an abrupt increase in the internal resistance of the first PTC element 56 and the second PTC element 57 based on the overload current flowing through the motor.

When an external force is forcibly applied to the shaft 2, for example, when a person grasps the stay 1 and forcibly rotates the shaft 2, the outer mirror collides with an obstacle and a large force is applied to the shaft 2. In this case, the engagement projection 22b of the clutch holder 22 pushes the cylindrical drive gear 23 upward against the upward urging force of the spring 24, and the rotation transmission engagement between the disk-shaped clutch holder 22 and the cylindrical drive gear 23 is performed. It is released. This prevents the drive mechanism 27 from being broken, the shaft 2 from being damaged, and the like.

According to the present invention, when the cylindrical drive gear and the disk-shaped clutch holder rotate relative to each other, only the arc-shaped sliding portion slides on the meshing engagement portion of the disk-shaped clutch holder,
Moreover, the arcuate sliding portion is formed on the inner peripheral side near the shaft, and the meshing engaging portion of the disc-shaped clutch holder contacts the arcuate sliding portion only on the side near the rotation center, so that the cylindrical drive is performed. Since the gear and the disk-shaped clutch holder rotate relative to each other, the relative rotation between the cylindrical drive gear and the disk-shaped clutch holder is stabilized. In addition, since the contact area between the cylindrical drive gear and the disk-shaped clutch holder is smaller than before, the sliding resistance can be reduced.

[0028]

Since the outer mirror device for a vehicle according to the present invention is constructed as described above, the sliding resistance during the relative rotation between the cylindrical driving gear and the disk-shaped clutch holder is reduced, and the sliding resistance is reduced. And the effect of reducing the output of the drive motor, and consequently reducing the size and cost.

[Brief description of the drawings]

FIG. 1 is an exploded perspective view showing a main configuration of a vehicle outer mirror device according to the present invention.

FIG. 2 is a sectional view showing the internal structure of the vehicle outer mirror device according to the present invention.

FIG. 3 shows a vehicle outer mirror device according to the present invention;
It is the top view seen from the upper part before attaching a stay.

FIG. 4 is a bottom view of the shaft according to the present invention.

FIG. 5 is a partially enlarged view showing a sliding contact relationship between a ball and a guide groove of a flange portion according to the present invention.

FIG. 6 is a sectional view taken along line AA of FIG. 10;

FIG. 7 is a sectional view taken along the line BB of FIG. 10;

FIG. 8 is a perspective view of an upper case according to the present invention.

FIG. 9 is a plan view of the upper case shown in FIG. 8 as viewed from above.

FIG. 10 is a plan view of the upper case shown in FIG. 8 as viewed from below.

FIG. 11 is a plan view of a state in which a drive mechanism is incorporated in an upper case according to the present invention as viewed from below.

FIG. 12 is a rear view of the case according to the present invention as viewed from the vehicle body mounting surface side.

FIG. 13 is a perspective view showing an example of a vehicle body mounting bracket according to the present invention. It is.

FIG. 14 is a sectional view of the disc-shaped clutch holder shown in FIG. 1;

15A and 15B are explanatory views of the cylindrical drive gear shown in FIG. 1, wherein FIG. 15A is a plan view thereof, FIG. 15B is a cross-sectional view taken along line CC, and FIG. 15C is a partial perspective view thereof. .

FIG. 16 is an explanatory diagram for explaining the meshing engagement between the cylindrical drive gear and the disk-shaped clutch holder,
FIG. 15A is an explanatory view of the meshing engagement state, and FIG.
(A) is a cross-sectional view along the line C'-C ', (b) is a partial cross-sectional view showing the meshing engagement between the cylindrical drive gear and the disk-shaped clutch holder, and (c) is the meshing disengaged state. 15 is a cross-sectional view taken along a line C′-C ′ in FIG.

FIG. 17 is a sectional view taken along line DD of FIG. 10;

FIG. 18 is a perspective view of the plate member shown in FIG. 1 as viewed from above.

FIG. 19 is a top view of the plate member according to the present invention.

FIG. 20 is a side view of the plate member according to the present invention.

FIG. 21 is a perspective view of a plate member according to the present invention as viewed from below.

FIG. 22 is a bottom view of the plate member according to the present invention.

FIG. 23 is a sectional view taken along line EE in FIG. 22;

FIG. 24 is a sectional view of a joint member according to the present invention.

FIG. 25 is a plan view showing a fitting relationship between a joint member and a worm gear according to the present invention.

FIG. 26 is a sectional view taken along line FF of FIG. 22;

FIG. 27 is a plan view of a lower case according to the present invention.

FIG. 28 is a sectional view taken along line GG of FIG. 27;

FIG. 29 is a view of the lower case according to the present invention as viewed from the vehicle body mounting side.

FIG. 30 is an exploded perspective view showing a worm gear and a washer according to the present invention. It is.

FIG. 31 is an exploded perspective view showing another example of the worm gear and the washer according to the present invention.

FIG. 32 is a side view showing an attached state of the worm gear shown in FIG. 30.

FIG. 33 is a side view showing an attached state of the worm gear shown in FIG. 31.

FIG. 34 is a bottom view of the lower case according to the present invention.

FIG. 35 is a sectional view taken along the line HH in FIG. 27;

FIG. 36 is a sectional view taken along line II of FIG. 27;

FIG. 37 is a circuit diagram of a drive circuit according to the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 2 ... Shaft 3 ... Upper case 6 ... Flange part 11, 12 ... Ball guide groove 13 ... Ball 18 ... Stopper member 18a ... Engagement plate part 22 ... Disk-shaped clutch holder 22b ... Engagement protrusion 23 ... Cylindrical drive gear 23e ... Opposition Surface part 23f Arc-shaped sliding part 28 Motor 30 Plate 31 Worm gears 31a and 31b Shaft part

──────────────────────────────────────────────────続 き Continued on the front page (56) References JP-A-8-34290 (JP, A) JP-A-4-63738 (JP, A) JP-A-6-87074 (JP, U) JP-A-2-34 49638 (JP, U) (58) Fields studied (Int. Cl. ⁷ , DB name) B60R 1/00

Claims (1)

(57) [Claims] A shaft (2) that carries an outer mirror and is rotated between a use position and a storage position is supported by a case (3) fixed to a vehicle body. A rotation transmission mechanism for transmitting the rotation of the drive motor (28) to the shaft (2) is provided, and the rotation transmission mechanism is rotatable relative to the shaft (2) and is rotatable relative to the shaft (2).
8) a cylindrical driving gear (23) driven by the driving mechanism and an engagement engaging portion (22b) engaged with the cylindrical driving gear (23) from the axial direction thereof by the urging force of a spring (24). And transmitting the rotation of the cylindrical drive gear (23) to the shaft (2) during meshing engagement, and rotating the cylindrical drive gear (23) during non-meshed engagement.
The disk-shaped clutch holder (2) cuts off the rotation transmission of the cylindrical drive gear (23) by rotating relative to
2), wherein the cylindrical drive gear (23) has an opposing surface portion (23) opposing the meshing engagement portion (22b).
e), and the opposed surface portion (23e) has the disc-shaped
When the latch holder (22) is relatively rotated, the engagement
The arcuate sliding portion (23) with which the mating portion (22b) comes into contact and slides
f) and the relative rotation of the disc-shaped clutch holder (22).
A gap is formed between the meshing engagement portion (22b) during the rotation.
An outer mirror device for a vehicle , comprising: an arc-shaped recess (23g); and the arc-shaped sliding portion (23f) is formed on a side closer to the shaft (2).